Power transmission



Jan. 9, A1940. JQ JANDAsEK POWER TRANSMISS ION Original Filed Aug. 14, 1930 6 Sheets-Sheet 1 `INVENTOR l Jan. 9, 1940. J, JANDASEK 2,186,025

POWER TRANSMISSION Original Filed Aug. 14, 1930 6 Sheets-Sheet 2 :ELSE INVENTOR l.Im1.9, 194o. I J, JANDASEK 2,186,025

PQWER TRANSMISSION Original Filed Aug. 14, 1930 6 Sheets-Sheet 3 INVENToR Jan. 9, 1940. J. JANDAsEK POWER TRANSMISSION Original Filed Aug. 14, 1950 6 Sheets-Sheet 4 fig-2U Jan. 9, 1940.

Y J. JANDASEK POWER TRANSMISSION original Filed Aug. 14, 195o 6 Sheets-Sheet 5 lil fZZ W INVENTOR /mwa Jan. 9, 1940.

PoWER TRANSMISSION Original Filed Aug; 14, 1950 6 Sheets-Sheet 6- INVENTOR;

JANDAsl-:K 2,186,025 I Patented Jan. 9, 1940 aisaozs POWER 'mANsMrssloN Joseph Jandasek, Cicero, Ill.

Application August 14, 1930, serial No. 475,278

Renewed January 25,1937

34 Claims.

This invention relates to a new apparatus for transmitting power from a primary or power generating member to a secondary or driven member in such a way that while heavy torque is 5. produced in the secondary member, at low speeds of the secondary member, only part of the energy generated by the primary member is absorbed by the secondary member, vand the remaining energy is returned to the primary member, producing an auxiliary torque acting in the direction of the rotation of the said primary member and in this way reducing the torque which is necessary for driving the said primary member. In other words; at overloads the function of the primary member isy partly as a driving member and partly as a driven member. At high speeds of the secondary member, however, the function of the primary member is that of-a generator only.

Energy istransmitted by means of energized fluid from the generating member to the motor, where at normal loads all of the said energy is consumed, but at overloads only part of the said energy is consumed, while a maximal torque is 4produced in the said motor and the remaining part of the said energy is transmitted back to the said generator by means of the said uid returning ducts, which are designed in such a way that auxiliary torque is produced in the said generating member in a manner that helps to propel the generator. At lo'w speeds of the motor the pressure energy of the circulating fluid is not consumed by the said motor and additional pressure energy is created from velocity energy of the fluid by the said motor, consequently the circulation increases at low speeds. At high speeds of the motor, however,- pressure and velocity energy of the fluid are absorbed by the motor and consequently the circulation, i. e.,'quantity of the said fluid per second, decreases. Torque produced in the said motor increases directly' with the quantity of the circulating fluid, hence at low speeds a heavy torque in-the motor is created,

while at high speeds a light torque is produced.

' The main difference between the present idea and the idea described in my Patent No. 1,855,967 is: according to the present idea the increase of the torque is mostly due to the increasedjquantity of the circulating iiuid, while the speed of the generator can. be kept substantially constant. According to the previous idea increase of the torque was mostly due to the increased speed of the generator and more effective fluid energizing action of the said generator. It 1s apparent that. an apparatus can be designed combining both ideas, so that the increase of the torque obtained would be due to the increase in the quantity of the circulating fluid as Well as due to the increased speed of the generator and the more veilective energizing action of the same. The previous idea also employed for overloads an auxiliary driven member, properly connected to the generator, while in the present idea the said auxiliary. member is not used'but the remaining part of the energy which was not consumed by the motor is absorbed directly by the generator itself.

To attain these and other objects I have interposed in my turbotransmission between the outlet from the turbine runner and the inlet of the pump impeller for adjustable guiding member (in Patent No. 1,855,967 the main set of redirecting vanes is nonadjustable).

Another object of my invention is to provide a new combination of the above mentioned turbotransmission with a reverse gear and-to provide a practical and easy to operate method for controlling the said transmission and the reverse gear.

It is also an object of the invention to stop the circulation of the fluid, in order to prevent any drag between the impeller and the turbine runner so the reverse gear may be meshed without shock or slid out of mesh easily.

Other objects of my invention are: by turbotransmission is designed to be a completely enclosedy and independent unit, fastened to the e'ngine by a few bolts, each shaft ofthe transmission is supported by'two bearings only, which assures perfect alignment of the bearings without expensive extra accuracy in the manufacturing. Reversing in my transmission is controlled by foot and the operators hands are free. MY transmission is made eicient by selecting the proper curvature` and shape for the Vanesa and by designing all uid channels in a way that the energy can be returned to the pump and not be lost on its way.y The pump and turbine are balanced hydraulically to do away with axial thrust.

Some of the many possible embodiments of the invention are illustrated in the accompanying drawings, each consisting basically of a driv` ing and a driven member and guide varies, in which- Figure 1 is a longitudinal section of a turbotransmission combned with reverse gear'constructed in accordance with my invention. l,

Figure 2 is a vertical section o'f the transmission taken on line 2--2 of Figure 1, showing the arrangement of the gears and the operating pedals.

Figure 3 is a perspective view of a pad which operates a latch on guide vanes controlling lever. Figure 4 is a latch assembly.

Figure 5 is' a. vertical section of one half part of the turbine runner assembly, Figure 6 is an elevational view of the same runner; Figure 7 is a vertical section of one half part of the pump impeller assembly and .Figure 8 is an elevational view of the same impeller.

Figure 9 is a vertical section -of the guide vanes assembly and Figure 10 is a. section and view taken on line IO-III-I-ID of Figure 9 showing the same vanes assembly.

Figure 11 is a perspective view of a free vane used in guide vanes assembly; Figure 12 is a perspective view of lever clamped on guide vane pinion shaft.

Figure 13 illustrates the curvature of the runner vanes as well as uid velocity diagrams, left diagrams are for overloads, right diagrams for light loads; Figure 14 shows impeller vanes and velocity diagrams, again the left diagrams are for heavy loads and right for light loads. Figure 15 represents the prole of the guide' vanes and their velocity diagrams.

Figure 16 illustrates combined velocity diagram for the impeller discharge and for therunner entrance at heavy and at light loads.

Figure 17 is a Vdiagram showing the speed, horsepowers and torque of the bine runner.

Figure 18 illustrates diagrammatically an arrangement of a reversible device equipped with one impeller, but two sets of runner vanes and two sets of guide vanes.

Figure 19 is an elevation view showing. runner vane as it would be if it were rotated about the axis until it lay in the plane of the paper, and does not show actual projections.

' Figure 20 is a section through the runner vane taken on line A, B, C, D, E of Figure 19 and showing the actual curvature of the runner vane. Figure 21 is a view of the same vane showing' the actual projections 'Figure 22 is a vertical section of one half part of the pump impeller; Figure 23 is a side View of Figure 22. l i

Figure 24. illustrates another form of turbotransmission designed according to my idea where the propeller type of impeller and runner are used.

Figure 25 is a sectional view diagrammatically illustrating a form -of my apparatus where the impeller servesas a casing and runs in the open. y

Figure 26 illustrates an arrangement of my d evice with the guide vanes and their adjustment located on the sidi. of the primary shaft.

Figure 27 is a half vertical section illustrating a form of my device equipped with `two sets of guide vanes and two setsof -runner vanes for the purpose of reversing.

'Figure 28 is a longitudinal section illustrating another form o f the turbodevice with'reverse'.

gear. i Y Figure 29 shows a side view of the forward pedal and Figure 30 is a' side View of the reverse pedal.

Figure 31 is a rear elevation of latch lever assembly.

Figure 32 is a diagrammatic development illustrating the ideal curvature of the vanes and the direction of thefluid flow at overloads. Figure V33 shows the shape of the same vanes: and the direction of the fluid flow at normal loads.

impeller and tur- Figure 34 is a sectional view showing a form of myvdevice equipped wiii a two stage turbine rotor. Figure 35 is a diagrammatic sectional View representing a form where not only the guide vanes but the runner vanes are pivotedly mounted to their webs and shrouds.

Figure 36 is a sectional view illustrating a device in which the turbine rotor has two sets of passages to either of which the liquid may bev` guided by shifting the rotor axially.

Figure 37 represents diagrammaticaliy my apparatus equipped with an axially shiftabie, not rotatable, guide wheel interposed between the outlet of the impeller and the inlet of the runner, for the purpose of reversingl Figure 38 is a diagrammatic view showing: on the right hand side the curvature of the vanes through which the operative` medium iiows in the circuit formed when the guide wheel of Figvure 37 is in location forv forward, on the left hand side showing the curvature of the vanes through which the operative medium flows in the circuit formed when the guide wheel of Fig-vv pump; all three of the said parts-arranged in such relative positions that their passage systems form the circuit in which a iiuid circulates.

'I'he primary or secondary shafts may be arranged in any desired relative positions, the most important being coaxial.

The invention will be fully understood by referring to the accompanying drawings, forming a part of this speciiication, in which:

Figures 1 and 2 illustrate a form of my hydraulic apparatus equipped with a reverse gear and proper control, this apparatus being especially suitable for the propelling of vehicles. The numeral indicates the main part `of the fluidtight stationary casing to which a cover 5l is fastened by bolts 52; easing' 50 is rigid1y secured to aJ ily-wheel housing 53 of a power engine by cap 4screws 54. The casing 50 is provided with stufling-box 55 and with ball bearing 56 for driving shaft 51, which shaft is secured by means of a spline 58 to a Vflange 5 5; preferably this flange and the said shaft are so connected as to permit relative longitudinal movement, but prevent relative rotarymovement, this is in orderV to facilitate manufacturing, assembling, and installation of vthe device. The ilangeis fastened to a fan shape flywheel 60 by means of bolts Il;

the flywheel blows the air against e casing 50 in order to cool it. Mounted on the shaft 51 by bolts 62 is an impeller assembly, (see also Fig. ures 7 and 8) consisting of: an impeller shroud 63 integral with vfixed blades 64 (see also Figure 22 and 23)', an impeller web 55 attached to the shroud by bolts 56, an impeller disc. fastened to the web by bolts 58; a set of semilfree vanes 59 rotatably mounted on bolts i5, pivoted at their leading edges, adjacent to the outlets from the guide vanes, and capable of adjusting themselves to the direction of discharge from the lguide vanes; the inclination of the vanes 59 .is limited on both sides by capscrews VII and 1I; which or impact to the discharge side of the said asl sembly, where it is delivered through adjustable vanes 11, to the primary element or pump. Screws 18, projecting into the guide vanes channel serve as stops and limit the movement of vanes 16 (see also Figure 15). The said vanes 16 :are equipped with ribs 1,8 to increasetheir fluid guiding effectiveness. The eccentrlcally pivoted vanes 11 are rigidly connected to pins 88 by means by keys 8|; each pin 88 is integral with a spur gear pinion 82, and is pivotedly supported at one end by shroud 14 and by web 13 at the other. end; one of the said pins is.

I equipped with a projection 83 and stuilng-box 86 in the cover 5|, to which projection a lever 84 is rigidly clamped. (For detail see Figure 12.)

^ The said projection also serves as a pivotal support for a latch lever assembly |3|. (For detail see Figure 31.) Allspur gear pinions 82 are in mesh with a ring spur gear 85 which is kept in position by a ring 86, said ring being bolted to the cover by screws 81. All vanes 11 must rotate simultaneously around their axis because all the pinions are connected by the ring` gear 85; every position of the ring gear corresponds to a certain position of all the guide vanes. It is to be noted that the centerline of the semifree vanes 16, when at action, is not parallel toV flow, angle A" in Fig. 15, left, but the vanes 16 are at an angle to the flow in the same way aS an airplane wing possesses an angle of incidence. Without this angle the vanes 18 would not deect the flow and would be useless. For this reason also the vanes 16 have a smoothly rounded entrance edge, being of a teardrop shape.

In reference to gates: in order -to relieve thev impeller sufliciently at heavy loads, the discharge angle D" of the gates must be .comparatively small: in 'order tohforce the fluid to follow this small angle, the actual length X of gates must be large in proportion to their radial height Z where radial height Z equals: R"d-R. Fig. 1 5 shows gates v11 having length X more than 3(R"d-R").

By the use of adjustable guide vanes 11, the driver of the'vehlcle can load up or unload the pump (consequently the engine), as much as it is necessary, because it is possible to change the directing angles and channel area ofthe guide vanes so that they correspond to a certain quan-l tity of passing fluid; it is possible to4 stop the flow entirely in a similar way as'it is accomplished on water turbines.

The .runner assembly (see also Figures 5 and 6) consists of web 81,' equipped with slots 8| at periphery and 92 at hub for vanes 83, shroud 88 and bolts 38, fastening the whole assembly together. Each vane 89 (see Figures 19, 20. 2l)

is provided with lug 93 to flt slot 8|, and lug 84 to fit slot 92 in the web 81 for the purpose of securing the said vane rigidly in the correct location.

The runner assembly as a whole is secured The cover 5| serves also as a case for the re.

verse gear, which can be of any well known construction, but I prefer asliding change gear type in which the gear is'shifted by foot pedals of my own construction. A third shaft |82, is supported by ball bearings |83 and |84, the latter bearing secured by a nut |85, is carried through a stuffing box |88 in the c'ase 5|, and is provided with a taper fitting |81 for the attachmg 'of a propeller shaft (not shown) for a vehicle'drive. The shaft |82 carries a sliding gear |88, shifted axially by a fork |88 on shift rod ||8 equipped with slots and secured in the proper position by b all ||2 and spring H3.

The gear |8| meshes with an idler gear ||4 and this in turn meshes with a double gear 5 and ||6 carried on roller bearings ||1 and ||8, which are supported by. a large pin Il! secured in the case 5| by bolt |28.

The gear |88 is equipped with jaws |2| which mesh with the teeth of gear |8I, if the said gear 88 is shifted axially for direct drive; or the teeth of gear |88 mesh with the teeth of gear 6 when gearl |88 is shifted backward for jreverse drive.

According to my invention shifting of the gea |88 is accomplished by means of two foot pedals: |22 (see also Figure 29) is marked F and is the forward pedal; reverse pedal 23 is marked' R (see Figure The pedal |22 is rigidly secured to a shaft |24 which is integral with a lever |25 operating a bolt |26 of the fork |88. 'I'he pedal |22 is integral with an external spur gear segment |21 and pedal |23 is integral with an internal spur gear segment |28, both segments |21 and |28 being in mesh with a spur gear pinion |25 integral. with a freely rotatable shaft |38. In this way, when pedal |22 is pressed for- Ward,v the pedal |23 rotates backwards, and lever |25, fork |88, ,and gear |88 move forward and vice versa, when the operator steps on pedal |23 the gear |88 is shifted into reverse. In Figure 2 I have also illustrated the relative positionof these pedals to a brake pedal marked B" and to an accelerator pedal marked A of an automobile. Shifting pedals F an R are to be operfree from shifting work which is especially im portant in the case` of motor busses.

Control of the guide vanes is accomplished by a latch lever |3| (see also Figure 31), levers |3| and-184 turnabout pinf 83 as a common pivot axis. Ordinarily a tension spring |38 pulls lever |3| down until it presses upon a lug |38 of the lever 84. In this way the spring |38 closes guide vanes 11 against the pressure of the fluid in the guide vanes channel. Whenever the pressure ofthe fluid overcomes the tension of the spring |38 vanes 11 open automatically and vice versa. When the operator presses down lever (Figure 3) he pulls a latch rod |32, compresses the spring |34, and' presses down lever |3| which in turn presses upon lever 84, which finally closes vanes 11 with the effect of unloading the pump and speeding up the engine. If the operator presses on the latch lever very hard he can close the fluid circuit entirely; which enables the shifting in reverse without the need of any clutch.

For the control of the guide vanes for large power transmissions a servomotor of' similar construction Vas that used on turbines could be employed.`

Because of the friction and the eiliciency of the drive on lo'ng nonstop trips it is a great advantage to eliminate the action of guide vanes 11. Without guide vanes vmy torque converting device becomes a mere hydraulic clutch mechanism where the torque on the third shaft is -at all times the same as that of the primary shaft which gives all the advantages of direct drive, being a very economical device. At high speeds the fluid needs but little retardation of the driven member to develop the required driving torque, hence the lag or slip between the driving and driven members is insigniiicant, about 2 vor 3%.

This elimination of guide vanes is accomplished by pulling up the lever |35 and |3| until the latch |33 catches the lug |31 of the case 5l, and holds the lever |3| in its up position. In that way lever |3| does not press upon lever 84 and eccentrically pvoted guide vanes are free to ad- Just themselves to the rate and direction of discharge from the turbine so th'at the fluid -iiows through the said guide vanes without shock or impact.

Whenever the operator feelsthat additional torque might be required, he steps on the lever |35, pulls the latch |33 from engagement with the lug |31, and a tension spring pulls lever III down, which presses upon lever 8l and this turns guide vanes 11; in this way additional torque can be created and my device becomes a torque converter again.

With reference to -the velocity diagrams, well known from textbooks on turbines 'and centrifugal pumps (see Figures 13, 14, 15), the following notations will be employed:

For the impeller:

J--Velocity of iiow (radial) v-Absolute velocity of iiuid.

w-Velocityof iiuid relative to the impeller.

u -Linear velocityof a point of the impeller.

r-Radius to anypoint of the impeller from the axis of rotation.

a-Angle betweentv and uat entrance.

b-Angle between w' and u at entrance.l

c-Angle between w and u at discharge.

fla-Angle between v and u at discharge.

s-Tangential component of v, which equals v cos a at entrance or v cos d at discharge.

l-Area of ow normal to f.

q-Pounds of iiuid flowing per second.

h-He'ad of iiuid imparted.

t-Torque exerted.

n-Revolutions per'niiiute.

g-Acceleration of gravity.

--Energy imparted by impeller.

For the runner same notation will be used but in capital letters: F, V. W, etc.

For the guide vanes capital letters with a superscript thus F", V", etc., however, it must be remembered that linear velocity U" equals zero.

The superscript will refer to the stream at entrance and the superscript (d) at discharge.

In reference to the fixed-impeller vanes M, see Figure 14, I prefer back curved vanes because they help the impeller to keep its speed at heavy loads as will be shown later. .Heating vanes 3l serve as driving vanes at light loads and high speeds (see Figure 14, right) the velocity o! the 'incoming iiuid being less than the rotating speed of vanes Il. At heavy loads, however,` the iluid after discharge from the guide vanes. At heavy loads the function of the impeller is partly as the action of a reaction turbine.

Numeral A indicates the ideal flexible runner vanes and numeral 'I1 shows the ideal flexible guide vanes; notice lt the entrance edge of .vanes 11A is curved at heavyv loads, but is curved forward/jat light l A In reference to the/ runner vanes I3, they are more similar to the stationary guide vanes asused on the so-called turbine pump," for changing the water velocity into pressure, and are dissimilar to vanes as used today on the reaction type of water turbines.

The runner vanes in my device are divergent,

see Figures 13, 20,A 21, while on all known turbines of today,=` thel vanes must be convergent in order to make use of available uid pressure, and to absorb iluid energy. In my device the iiuid pressure behind the runner is greater than the fluid pressure in the circuit before the runner. This is especially true at low speeds when the circumferential component of the ilui'd is great.` In all reaction turbines, the fluid pressure after the runner is smaller than before the runner and on all action or impulse turbines the pressure after the runner equals the pressure before the runner. The discharging angle of my runner vanes is larger than the entrance angle because the runner vanes are similar to stationary guide vanes as used on turbine pumps, for changing fluid velocity into pressure. These guide vanes always have the discharge angle larger than the entrance angle. If this were not so, such guide vanes would be useless. In all known turbines the discharging vane angle' is smaller than the entrance angle for obvious reasons.

The discharging 'angle of my runner van (Figure measures about 75, while the largest discharge angle on all known economical turbines never exceeds The area of iiow L' normal to velocity W, relative to the runner, is smaller at the entrance than the area of iiow Ld normal to velocity Wd. at the discharge. 'Ihe relative velocity of iiow WI is also smaller than W, consequently the discharging angle of my turbine runner is greater thanfdischarging angle of all known turbines.

The increasel of pressure due to tlow between the runner blades ot my device can be calculated according to the following formula, taken from Gibsons- Hyradulics and its Applications", third edition, page 508.

' be remembered that any smaller than inlet angle.

design of divergent runner vanes (Figure 13, left, and Figure 20) is necessary for returning energy from the runner to the impeller, because the pressure P' forces the fluid through the guide vanes at such velocity as to unload the impeller -and to retain the speed practically constant at all loads (Figure 17).

To increase the efficiency I select the divergency of each runner vane relative to the next adjacent vane smaller than 30 at any point on the vane, even at the outlet where the divergency is largest.

In reference to the term divergency, it must fluid channel is divergent wherever the velocity of the fluid ow Wd atl the end of the channel is smaller than the velocity of the liquid flow We at the entrance of the channel. The same volume of liquidV must ow through the channel at the entrance as well as at the exit or at any point between the dentrance and the exit of the channel. The volume of the liquid flowing is equal to its velocity W, times the area of the channel L, which area is perpendicular to the flow. Then WL=W1L. If the discharging velocity Wd is smaller than entrance velocity We, the channel area Ld must be larger than Le. Whenever the discharge area LI of a channel is greater than the entrance area Le, that channel is referred to as being divergent with respect to area. The channel area consists of two dimensions, that is, width vand depth. Since width times depth equals area, the channel can be divergent when- A, both dimensions are divergent; B. when one dimension is divergent and the other dimension is neutral or parallel; or, C, when one dimension is convergent and .the other dimension is divergent, but'the divergent dimension is such as to more than offset convergent dimension. It thus appears channel can be divergent in respect to area even if the channel is convergent in respect to one dimension. D

In Figure 13 I have illustrated the increasing curvature and increasing divergency of the runner vanes. The width of the channel at the entrance equals the pitchxsin B, while at the discharge the width of the channel equals the pitch Xsin C. As illustrated in Figures 13 and 20, the angle C is more than twice the angle B. The width of the channel at the discharge must therefore be greater than the width of the channel at the inlet.V Expressed in a different way, a channel in a radial turbine is divergent with respect to width when the discharge angle is greater than inlet angle. respect 'to width when the discharge angle is The discharging velocity Wi is less than entrance velocity We when the fluid channel is divergent with respect to area, and vice versa.

Divergency of a channel at any point between the inlet and the exit is measured by the angle of the channel walls at that point, or by the increase of the channel area per unit length of the channel. This angle of the channel wall divergency must not be more than 30 at any point, and should be smaller, especially for high iiuid velocities. The curvature of the vanes should also be gradual or small for high velocities, but can .be progressively increased as the velocity decreases. This new method of designing turbine vanes divergently rather than convergently, with the` inlet angle smaller than the outlet angle, is one of the important features of the present invenand is convergent with tion, because in practice only one, or at the most two, sets of semi-free vanes 16 can be used because there is insuilcient space. 'Ihe -entrance angles of the semi-free vanes on the guide wheel cannot therefore be correct for all fluid discharge angles of the runner but must` be a compromise.

According. to my method, the changes of the fluid discharge angles at the turbine outlet can be decreased, and only a limited number of semifree vanes employed while the shock losses are` minimized. i

For example:

A. Assume that for high speed the divergent turbine vanes have an angle of discharge C==80" and angle D= When starting, angle D equals 180-80 (U=0). Then the total change of the angle D from starttov high speedA will equal (180-80l -15=85.

B. At high speed a reaction turbine has a discharge angle C=15 and angle D=15. When starting, (U=o angle 12:18'045, and total change of angle D from the start to high speed equals (180-15) -15=150, which is almost double that of the divergent vanes in Example A.

The smaller the discharge angle differences the smaller will be the dierences of uid entrance angle A" (Figure 15), andthe smaller the shock losses. Consequently, divergent turbine vanes are more economical for turbine transmission with variable speed than customary convergent vanes. It will be understood, of course, that thev discharge angle can b'e varied as required for various designs. For literature on reaction or impulse turbines, see, for instance, Gibsons ,Hydraulics and its Applications, pages 441-454, 456-462, 467-478, and 500-520.

At overloads only part of the iluid energy is consumed in the turbine and the remainder of the energy is transmitted to the guide vanes, and from the guide vanes back to the impeller. This is the chief reason that I employ vanes having discharge angles greater than 45 (Figures 13 and vanes having the discharge angle larger than the intake angle; divergent vanes having the angle ofv vane divergence small at points of high uid velocities, but with the angle of vane divergence greater at points of lower velocities; vanes having small curvature at inlet, but with larger curvature at outlet, and in the shape of a parabola. At low speeds the pressure energy of the fluid is not consumed by the turbine and additional pressure energy is created from the velocity energy of the fluid by the turbine vanes having discharge angles greater than 45 and greater than the inlet angle. This uid pressure forces the fluid through the guide vanes in the same way that fluid pressure forces water through the gates of a hydraulic turbine at such velocity as to transmit fluid energy not absorbed by the runner back to the impeller, and in that way unload the impeller.

Redirecting guide vanes must, however, be interposed between the runnerdischarge and the impeller entrance to preventthe uid from entering into the impeller in the opposite direction and thereby overload the impeller. The fluid pressure causes the oatingvanes 69 to act as driven vanes at heavy loads (Figure 14, left), because the uidvelocity entering the impeller becomes greater than the speed of vanes 69. Due to the pressure increase combined with the force exerted by the redirecting vanes located between runner outlet and impeller inlet, the action at That is why 15 the runner vanes 89 are similar in shape and function to the stationary guide vanes as used on turbine pumps, for changing fluid velocity into pressure.

The ordinary water turbine vane angle at entrance is larger, the vane angle at exit is small, because the energy of the discharged water should be as small as possible. In my device, however, at overloads the fluid energy is not absorbed entirely in the runner and therefore must be transferred back to the pump. If redirecting vanes could be made perfectly exible and have correct angles at all speeds (see Figures 32, 33) f the exit angles of the runner vanes could be small. As, however, the vanes are not flexible there would be a great loss at heavy loads, where the fluid discharging from the turbine would stream backward and strike against the guide vanes at a wrong angle. It is better in my device to change a great part of the velocity energy into pressure energy and thus avoid shock losses due to wrong vane angles. Therefore, I prefer runner vanes with a small entrance angle and with a large exit angle (see Figure 20, which illustrates a vane with entrance angie smaller than 45 and with discharge angle about 75); in order to make this change of velocity into pressure as economical as possible vanes 89 have a large radius of curvature (small curvature) at the entrance, but a small radius of curvature (large curvature) at the exit, so the angle of vane divergence is small at points of high fluid velocities; at points of lQw fluid velocities, the angle of\vane divergence can be greater and the elciency of the velocity to pressure change is not effected much, because internal friction losses are in proportion to the square of the fluid velocity. That is why I have designed my turbine vane with increasing curvature, in the-shape of a parabola. Also, according to the multi-dimenslonal theory, the natural flowing process follows a path in the form of a parabola when changing its direction in the runner.

Figure 19 is an elevation view showing the runner vane 89 as it would be if it were rotated about the axis Auntil it lay in the plane of the paper. In Figure 20 is illustrateda section through the runner vane 89 taken on line A,"B, C, D, E of Figure 19 and shows how the radius 'of curvature decreases toward the exit point E; points A, B, C, D, E were all lying on a parabolic curve, vwhen the diameter of the runner was infinitely large. In Figure 21 is drawn a view of the same vane showing the actual projections of the vane for the runner diameter of ilnite size. A BB', CC', DD', EE', in Figure 20 are equal to corresponding arcs BB', CC', DD', EE', in Figure 21. It is also important that the discharge from the runner is axial and of the smallest possible diameter so the angle of the outcomingiluid now varies only little at different speeds, vin order to eliminate shock losses in the guide vanes. In op' eration, refer to Figs. 13, 14, 15, when the working fluid enters the runner vanes. its velocity has a powerful circumferential component and an axial component; but,.at high speeds, the runner vanes are working at full capacity and they extract all the energy of the fluid which was imparted by the impeller vanes, and the uid leaves the runner vanes with a' velocity which has a diminished circumferentiak component in Athe direction of rimner rotation, and, of course, an Y axial component. 'Ihe fluid now 'passes through the guide vanes which do not substantially alter the direction of flow so that the fluid when leaving the guide vanes and returning to the impeller vanes possesses a velocity which has the same circumferential component as the velocity at the runner discharge; in other words the guide vanes do not function.

At very low speeds or when starting, however, the runner vanes are not extracting all the energy of the fluid which was imparted by the impeller vanes, and the fluid leaves the runner vanes with a velocity which has, substantially, an axial component only but possesses a great pressure energy, which was created from velocity energy of the duid by the diverging runner vanes, said runner vanes having a discharge angle about 75, as shown in Figure 20, or only slightly curved. The fluid now passes through the guide vanes which alter the direction of the ow and change the fluid pressure energy into kinetic energy, so that the fluid when, leaving the main guide vanes and returning to the impeller vanes ity which has again a powerful circumferential component. "The value of this circumferential velocity component can be adjusted or changed either manually or automatically, as described, so the device can pom both: high gearing ratio for oyesloads aswell as high emciency for normal load; ,L

From theY above it can be seen that the gist of my invention consists broadly in the provision of certain eillcient-means in a fluid power transmission comprising driving, driven and stationary,

vanes', to transform the fluid energy which was not absorbed'by the driven vanes into pressure energy and 'to change said fluid pressure energy by the stationary vanes back into velocity energy applicable directly to the rotation of the driving vanes. Entrance angles of the driving and stationary vanes are` automatically altered and corrected under the control of the fluid.

It can be .proved mathematically that in a turbine transmission with a fixed entrance angle of impeller vanes, the fluid will stream perpendicularly to impeller vanes when leaving guide vanes, and therefore all returning energy is lost by shock due to this wrong entrance angle; in other words, in fluid transmission with rigid impeller vanes at certain speeds no energy. can be returned to the driving vanes by means of circulating fluid due to improper guidance of the iluid. Therefore fluid alone, not energized, is returned to the driving vanes in such tons. In this invention, however, entrance angle of the impeller vanes automaticaly is corrected so the energy can be returned at all speeds and loads.

As known from textbooks, on hydraulics (see textbook Gibsons Hydraulics and its Applications, third edition, pages o-503, 629-632, D. Van Nostrand 0o.): A

Torque exerted by impeller equals:

t= q/a (md-rw) f 1) Power imparted by impeller equslsf l l eem/a) will-um) (s) Turning moment. of the runner equals:

' VT=(Q/U) (RSi-RS) (3) Power of runner equals:

' s= Q/a (visi-wss) (4) Turning moment of guide vanes reaction:-

T"= (Q/U) (R',"S"R"S"') (5) l -equals angle D" As there is no other source of power or of turning moment in our uid system, it is evident that: t|r+r"=o (o) and Torque of engine t is'almost constant within our operating limits. At low speed 8" is very small, due to angle D being large (see Figures 13, and 15), and can be neglected, further; A"=D and F=f.

flow velocity'f (L and D" being of a fixed value.) It also shows that T increases with ctg D" in other wordsl at smaller angle D", greater torque T can be developed.'

When angle D is selected too small, engine is :not loaded enough for' normal loads land rotates very fast which results in bad wear and tear of the yengine (too much energy is being returned to primary member).

Alsol when angle D" is selected small, thevelocity of discharge from guide vanes V" will be high and great"'losses due to friction will occur (Fig. 15).

At the large value of angle D", however, transmission will be very eiiicient, but only reasonable gear ratio of the transmission can be developed (not much energy is returned to primary member). For this reason I have designed adjustable guide vanes or gates in my device, so as to obtain efficient apparatus and still obtain large gear ratio. Discharging vane angle C" oi' guide varies and is variable, see Fig. 15; but this angle must be selected reasonably small, less than 45 so sufficiently great angular momentum could be imparted to the fluid; in the other case, when angle C" is too large, the impeller and of course the engine will slow down too much rand stall at heavy loads. y y

When latch lever 13| is lifted guide vanes 11 become free and their function is eliminated; in this case T"=0, consequently: t+T=0 (6A), in other words, the torque of the impeller is as great as that of the runner.

I have also curved the discharging impeller vane tips backward (see Figure 14) and the entrance runner vane tips forward. Explanation for this can be obtained by studying Figure 16.

In Figure 16 I have drawn a combined velocity diagram for discharge of impeller and for entrance of runner at heavy loads (ow velocity F is great). As there are no guide vanes between impeller and runner it must be: vd=V, and angle d'=A. A a

Wecan see now that for correct angles A, a and vane angles b, B, linear velocity of runnerUe must be relatively small to the velocity Vof the impeller ud and that is just what is required for a torque converter. At heavy loads the impeller rotates ata much faster speed than the runner.

In the same Figure 16 I have drawn a similar velocity diagram for a light load (value of- F is small) at right side. Here we can see that the are correst, i. e., my transmission works efciently at heavy as well as at light loads.

In Figure 17 I have illustrated graphically the advantages of adjustable guide varies as compared to'fixed vanes which are Adescribed in my 'Patent No. 1,855,967. Full line curves are for automatically adjustable guide vanes, and dotted line curves are for fixed vanes. Curve n represents the value of the speed of the impeller (R. P. M.) as theiiow velocity F increases for `,automatically adjustable vanes. Dotted curve n' illustrates the values of the impeller speed for xed vanes. It is apparent that at lighter loads (F is small) the speed of the impeller nf (or engine) is lconsiderably lower than at heavy loads (F large). In other words, when the fixed guide vanes are used at lighter loads the engine develops less horsepower e' which results'in smaller torque T' as compared to when adjustable guide vanes. are used. Inorder .to-obtain. a constant characteristic" ofthe device, i. e.,- where the speed of the impeller is practically constant-(see'curve n in Figure 17), the discharge angle D" of the guide vanes must be larger initially than the discharge angle'of the device illustrated in my Patent No. 1.855.967. lIn the device illustrated in the present application the impeller speed at the start is greater, and the angle D".must be smaller than the corresponding angleof the device illustrated in my copending application Serial No. 588,163, so the impeller speed at the start is greater in the device illustrated in the present application.

` As the turbine speed increases, this angle must decrease vby the amount Er which is the angle measuring the amount of change or adjustability in the discharge angle D" of the pivoted guide vanes. but the discharge angle must diminish slower than in the device illustrated in my copending application Serial No. 588,163. with a rising characteristic. therefore remain constant, instead of being variable, i. e., a decrease ofthe discharge angle D" for the device with a constant characteristic must be smaller than the decrease of same angle for a device with a rising characteristic". This is obtained by proportidning the strength of spring I 38 in proper relation to power of the iiow out of the gates.

This turbotransmission of itself does not provide a reverse motion; for the latter purpose a reverse gear is used,

Another very important item isthe problem of balancing axial thrusts.v No turbine or turbopump' 'is practical unless the axial thrust is balanced because enormous pressure can be pr- 'Ihe impeller speed will duced in the bearings which would endanger their j life, and decrease the reliability of the device.

In Figure 1 we can readily see that the side pressures of the fluid against the runner assembly would not be equal, due to the fact that entrance and discharge channels take part ofthe area on the right side of the web and consequently the total pressure on the right hand side is diminished.

The left hand side of the runner, however, is com'-` pletely under press/ure, spaces |40, |4I, |42. Hence the pressure against the runner assembly is acting on a smaller area,'portion |43, from the right, but acts on the larger area from the left, portions |40, |4|, |42. The result is that the unbalanced force tends to shift the runner toward the right. To prevent this tendency, a number of holes |44', |45, and |59 (see Figures 5 and 6), are drilled in the runner web to equalize the pressures on the right and left sidesof the runner. l

In order to decrease short circuit losses through openings |44, |45, and |59 and through portion |43, clearance rings |46, |41 on runner web 81, and clearance rings |48 |49, |50 on the impeller (Figure 7) and clearance ring |5| von the guide vane assembly (Figure 9) are provided.

The casing 50 is'completely filled with a fluid, this may preferably be oil. Leakage is prevented by stuffing-boxes and |52. From the standpoint of efliclent operation as well as commerclally the presence of a predetermined amount of fluid in the casing is imperative. However,v high pressure under heavy load, centrifugal force at high speeds, natural wear, poor packing or other sealing means around both shafts and other factors, tend to cause leakage from the casing. I have eliminated any stuffing-boxes of large diameters varound the sleeves, which are hard to keep tight due to the high periphery speed. Commercially such a leakage can be a sufcient reason for the failure of the whole machine. I have provided a simple, 'automatically acting means for delivering-the liquid tothe casing at all times during normal operation.

In order to prevent any leakage loss of oil the stuffing-box gland |53 is provided with an oil co1- lecting groove |54 to which is connected an oil drain pipe |55. The other end of pipe |55 runs into the gear case 5|. Oil level in the gear case is kept to a horizontal line' IBS-|56 which is located under the centerline of the shaft. Any oil which lpasses the packing in the stuing-box 55 is drained into the gear case 5|. The gear case 5| is also used as a reserve tank forthe fluid which is used in the transmitter.

The mechanism which delivers fluid to the casing 50 from gear case 5| consists of; pipe |51, check valve |58 and pipe |59 projecting into the casing 5|, at a point of comparatively small pressure, i. e., at the periphery of the guide vane web 13. The lower opening of pipe |51 is located right at the periphery of the constantly revolving gear H5; oil is driven into the pipe by the teeth of the said gear. The liquid will not escape from the case 50 through pipe |51 when the transmission is at rest, as the pipe |51 is closed by a check valve |58. K

Finally, I have designed my transmission so it would be an easy manufacturing proposition; for

instance, each shaft 51, 95, and |02 is'supported by two bearings only so as to keep them easily in line. 'The transmission as an independent unit is easily attached to the engine flywheel housing with a single spline 58 entering into the flange 59. My turbotransmission enables the automotive ,vehicle to be started by merely 'depressing the accelerator pedal A (Figure 2). Standing on a level, with the engine running at idling speed, theany jerks, because there Tis no rigid connection between the vehicle drive and the engine, there is also no clutch to shift.

All forward speeds of the car are controlled by the accelerator pedal only. 'I'he change of gear ratio (i e., the increase of torque) is automatic, since the increase ofthe loading at the road wheels slows the transmission and the runner moves mor slowly i'n relation to the impeller. The transmission, of course, can be stalled by overload, but the engine cannot thus be stopped; therefore the engine is protected from overloading"at all times. At idling speed the impeller does not pump sufficient iiuid into the runner to drive the vehicle. 'I'he vehicle commences to move as the accelerator is opened.

In Figures 18, 24, 25, 26, 27, 28, 34, 35, 36, 37, 38, 39, the-numerals |60 `up to |10 inclusive indicate the primary or driving shafts, which are 'connected to the power engines or other sources of energy (not shown). The numerals |1||8| inclusive indicate the secondary or driven shafts,

'numerals |82-| 92 inclusive indicate primary or third non-revolving redirecting guide blades and wheels; numerals 225-221 inclusive indicate stationary reversing vanes.

In Figure 37 the numerals 221 and 228 indicate ,I 'f

axially shiftable, but vnot rotatable, guide vanes, 221 for reverse drive and 228 for forward drive. Guide annulus 229 integral with vanes 221 and 2'28 can be shifted by means of lever 233 pivotally secured to a casing 23|, thereby bringing either of the vanes 221 or 228 into operation. The curvatures of the blades are indicated in Figure 38; it will be noticed that vanes 228 can be, omitted as the fluid has correct direction for forward" drive when discharged from vanes |9|. In Figure 18, primary blades and wheel |82 are axially shiftable for the purpose of reversing the rotation of the secondary shaft. In Figure 27, the whole, not rotatable, casing 232. is axially shiftable for the same purpose.

In Figure 36 runner'233 integral with vanes 206 and 201, is axially shiftable, thereby bringing either vanes 206 or 201 into operation, which results in very eilcient operation at all speeds and loads, because vanes 206/ are designed with curvature most suitable for high speeds and light loads, while vanes 201 are most suitable for low speeds and heavy loads.

In Figure 28 is drawna vcombination of turbotransmission with reverse gear. In this design the guide vanes are supported and secured against rotation by thin spokes 234 which are located in the space between the discharge from the impeller and the-'inlet of the runner.

In Fig. v39 I have illustrated a form of the invention comprising a stationary casing 240 enclosin'g a pump impeller |92, a turbine runner 209, and a stationary guide wheel 224 interposed between the exit from the runner and the inlet to theimpeller. The casing is provided with a sleeve 24| upon which the guide Wheel is freely mounted; a one way clutch 242 between the casing 24.0 and the guide wheel 224 permits rotation of the guide wheel in the same direction as the impeller and the runner rotate, but restrains the guide wheel from rotation inthe reverse direction.

WhatI claim is:

1. A turbine torque converter comprising a ating means.

2. A turbine torque converter comprising a passage for iluid including van impeller with blades, a turbine runner and a stationary guide wheel with one set of vanes and eccentrically' 'pivoted and movable gates, and means adapted to enable said gates to become free on their pivots and -adjust themselves to the direction of the uid, said impeller blades consisting oi two parts,

. one part being movable and the other part being iixed to the impeller.

3. A turbine torque converter comprising a passage 4for iiuid including rotary driving vanes, rotary driven vanes and stationary guide vanes, the driving, the driven and the guide vanes being coaxial and juxtaposed and forming a circuit in which the fluid is circulating and transmitting power,'said driven vanes being divergent and having a discharge angle larger than the entrance angle, said entrance angle'being approximately 40 and said discharge angle being approximately 75. A

4. A duid device for transmitting power having a primary blade wheel adapted to impart energy to a iluid, a secondary blade wheel having iiuid channels adapted to receive energy from said energized iluid and to convert the kinetic energy of the fluid into pressure energy, auxiliary means adapted to change the iiuid pressure into velocity and to redirect the fluid back to said primary means, said channels being designed to obtain an increase in pressure equal to (WL-Wm) /20 due to the ow through said channels, We representing uid velocity at the entrance. o f the channels and Wd being iluid velocity at the discharge of the channels, g representing acceleration due to gravity, said channels having-smaller divergency at inlet. and larger divergency at outlet, said .l0 channels having -smaller curvature at the inlet and larger 'curvature at the outlet, said channels further having the inlet angle smaller than the outlet angle, said outlet angle being greater than 45, openings in one of said blade wheels to balance axial thrust, and a small clearance ring on the last mentioned blade wheel to prevent short circuit losses 5. A fluid device for transmitting power having primary means adapted to Vgenerate energy in a iiui'd, secondary means having uid channels capable of receiving energy from-said energized .,iiuid, and also capable of changing kinetic energy of the iluid into pressure energy, third means being adjustable and having channels adapted to change the uid pressure into'velocity and to transmit part of the uid energy back to said primary means, the channel ofA the secondary.

means being designed so as to obtain increase in throughthehannels, and means adapted to control thevrate and direction of the fluid ow lof .the iiuid as well as at will. while in operation.

6. A fluid device for transmitting power having primary means adapted to generate energy ina uid, secondary means capable-of receiving energy from said energized iluid and also capable of changing kinetic energy of the fluid into pressure energy, third means adapted to change the iluid pressure into velocity and to transmit vpart of the iluid energy back to said primary means, and means adapted to eliminate the action of said third means, comprising mechanical means secured to said third means. iiexible means operating said mechanical means and means to disconnect said ilexible means from said mechanical means, at will, while in operation.

'1. A hydraulic apparatus for tatable primary blade .wheel with curved vanes transmitting vpower having a casing, iluid in said casing, a roadapted to energize the said uid, a'secondary rotatable-blade wheel with curved vanes capable of receiving energy from said energized uid, a

stationary guide wheel with gates adapted to guide the flow of said fluid in such a way that the iiuid enters the primary blade wheel moving in the same direction as that in which said primary blade wheel revolves, and means ladapted to change the outlet angle of said stationary gates automatically under the control of the iluid. also to change said outlet angle at will, while in operation.

8. A turbine power transmission comprising a passage for uid including a pump impeller with two series of vanes, a turbine runner and a guide wheel, the first series of said impeller vanes being capable of yielding to entering fluid, and means to limit said yielding to enable said vanes either to extract energy -from the iluid to impart energy to the uid or to .cease to function under the control of said uid, said iirst series oi.' vanes being of airfoil or teardrop shape, the impellerthe runner and the guide wheelbeing coaxial and juxtaposed and forming a circuit in which the uid circulates and .transmits power.

9. A hydraulic apparatus for transmitting power having a casing, fluid in said casing, a rotatable primary blade wheel with curved vanes adapted to energize said fluid, a secondary rotatable blade wheel with curved vanes capable oi receiving energy from said energized fluid, a guide wheel with gates adapted to guide the'ow of said fluid in such" a way thatl the uid enters the primary blade wheell moving in thesame direction as that in which the said primary blade wheel revolves, said guide, wheel having two-sets of vanes, the units of the first set being freely pivoted at `their leading' edges, adjacent to the outlet from the runner vanes, but equipped with stops so as to limit the angle of their inclinationv `in one direction, the units of the second set being eccentricallv. pivoted and adjustable. f

10. In a hydraulic apparatus for transmitting primary blade wheel adapted to energize the uid, a secondary rotatable blade wheel adapted to receive. energy from the energized fluid, a guide wheel adapted to change angular momentum of the fluid, said wheels forming a circuitin which the iluid circulatesV and transmits power, the primary wheel having two sets of vanes, the units ofthe rst set being freely pivoted at their leading edges-and equipped with two stops to limit the angles of inclination in both directions, the units of the second set being xed vanes.

11. In a hydraulic power transmission device,

the combination, with a primary shaft,.of'a secondary shaft coaxial with the said primary shaft,

to said turbine runner, a stationary casing containing duid and enclosing said impeller, runner and guide wheel, said impeller, runner and guide wheel having curved passages, which comprise the whole circuit in which said duid is circulating and power transmitting, several sets of openings in the runner web and several small clearance rings on said runner web, one clearance ring always being located between the two sets of openings, said openings to balance pressure on each side of the web, said clearance rings being provided to prevent short circuit losses.

12. In a motor vehicle, the combination with the engine dywheelv and the engine housing of the vehicle, a duid torque converter, said converter including a casing fastened to said housing. duid in said casing, a pump impeller connected to said dywheel, a turbine runner with substantially axial discharge, a redirecting guide wheel with movable gatesin said casing, each gate being eccentrically pivoted and carrying a spur gear pinion, all said pinions being in mesh with a common ring gear, means for turning said gates and said ring gear automatically under the control of the duid, and means for turning said ring gear operatively, at will, while in operation.

13. In a motor vehicle, the combination with an engine dywheel and the engine housing of the vehicle, a duid power transmission, said duid transmission having a casing, duid in said casing, blade wheels in said casing, a driving shaft connected to one of said blade wheelsa driven shaft connected to another one of said blade wheels, said driving shaft supported by only one bearing in said casing, the driven shaft being supported by one bearing in the casing, a double thrust bearing between said driving and driven shafts, and means connecting said driving shaft to said dywheel to permit relative longitudinal movement, but to prevent relative rotary movement, said casing being fastened to said housing.

14. A duid device for transmitting power having a casing, duid in said casing, blade wheels in said casing, some of said blade wheels having a plurality of series or sets of vanes, the units of some sets of vanes being freely pivoted at their leading edges but equipped with independent stops to limit the angles of their inclination, the first series of vanes being of airfoil or teardrop shape, said stops located in such a way that center lines of said pivoted vanes are at an angle to the dow in the same way as an airplane wing possesses 'an angle of incidence, said stops being independent from vanes of the 'other of said sets of vanes.

15. A turbine power transmission comprising a passage for duid including a pump impeller with a plurality of sets of vanes, a turbine runner, a guide wheel to increase the angular momentum of the duid, the impeller; the runner and the guide wheel being juxtaposed and forming a circuitin which 4the duid is circulating and transmitting power, at least one set of said vanes being of airfoil shape and being capable of yielding to entering duid, and means to limit said yielding, the plurality of sets-of vanes forming a one stage impeller, all of the sets of vanes being adapted 'to energize the duid. 16. A power transmission including driving means adapted to energize A'a duid, driven means adapted to receive energy from said duid, means adapted to redirect the duid from the driven means to the driving means, duid directing vanes dxed to the driving means, semi-free duid directing vanes carried by the driving means. stop means carried-by the driving means to restrict the movement of said semi-free vanes in two directions, duid directing vanes fixed to the driven means, semi-free duid directing vanes carried by the redirecting means, stop means carried by the redirecting means to restrict the movement of said semi-free vanes in one direction, adjustable vanes carried by the redirecting means, and manual means to control said adjustable vanes.

17. A power transmission including driving rotatable means adapted to energize a duid, driven rotatable means adapted to receive energy from said duid, third means adapted to redirect. the duid yfrom the driven means to the driving means, duid directing vanes fixed to driving means,

' semi-free duid directing vanes carried by the driving means, stop means carried by the driving means to restrict the movement of said semifree vanes in two directions,I duid directing vanes dxed to the driven means, semi-free duid directing vanes carried by the third means, stop means carried by the third means to restrict the movement of said semi-free vanes in one direction, adjustable vanes carried by the third means, manual means to control said adjustable vanes. a `casing surrounding the driving and driven means, apertures through one of the rotatable means to balance axial thrust, a driven shaft, said driven means being connected to 'said driven shaft, and means to collect leakage from the casing.

18. A duid device for transmitting power, having primary means generating energy in a duid. secondary means having duid channels receiving energy from the energized duid and capable of changing the kinetic energy of the fluid into pressure energy, third means having adjustable channels changing the duid pressure into velocity, said secondary channels being designed so as to obtain increase in pressure equal to due to the dow through the channels, where We represents duid velocity at the entrance of the channel, WYI the duid velocity at -the discharge from the channel, and n is acceleration due to gravity, said primary, secondary and third means being coaxial and comprising the circuit in which the duid circulates and transmits power and means to control the rate and direction of the duid dow by varying the area of the channels of the third means, so as to keep the speed of the primary means practically constant while in operation.

19. A duid device for transmitting power having primary means generating energy in a duid, secondary means receiving energy from the duid, third means changing angular momentum of .the duid, and means to eliminate the action oi the third means comprising mechanical means secured to the third means, dexible means operating the mechanical means, a casing containing the primary, secondary and third means, means fastened to the casing to disconnect the dexible means from the mechanical means at will while.

wheel adapted to change the angular momentum u 'the casing, some of the blade wheels having a plurality of series or sets of vanes, the units of some sets of vanes being eccentrically and freely pivoted but equipped with stops to limit the angles of their inclination, the stop members being located in such a way that center lines of the pivoted vanes are at an angle to the ow after engagement with one. of said stops in the saine way as an airplane wing possesses an angle of incidence, the stop members being independent from the vanes of the other of the sets of vanes.

22. A fluid power transmission comprising a passage for fluid including an impeller having a plurality of series of vanes, a turbine runner and a guide wheel, one series of the Aimpeller vanes being yieldable to the iiuid, and means -to limit the yielding movement to enable the vanes either to extract energy from the fluid or to impart energy to the fluid, under the control of'said fluid.

23. A fluid device for transmitting power hav- -ing a primary blade wheel imparting energy to a fluid, a secondary blade wheel having fluid channels receiving energy from the uid, a third wheel changing the angular momentum ofthe fluid, said wheels forming a circuit in which the. lfluid circulates and transmits power, the channels being designed to obtain an increase in pressure equal to (Wel-W) /2g due to flow through said channels, We representing uid velocity at the entrance of the channels and Wl representing fluid velocity at the discharge of the channels, y representing accelerationdue to gravity, saidA channels having smaller divergency at the inlet and larger divergency at the outlet, the outlet angle being greater than 45.

24. A power transmission including l driving means energizing iiuid, driven meansreceiving energy from iiuid, and third means changing angular momentum of the iiuid,'semifree fluid directing means carried by the driving means, stop means carried by the driving` means to restrict the movement of the semi-free vanes in two directions, semi-free uid directing vanes carried by the third means,y stop means carried by the third means to restrict the movement of the semi-free vanes.

25. In a fluid power transmission having a casing, means comprising a pump impeller having a set of fixed vanes and a set of. flexible vanes, a turbine runner and a guide wheel forming a power transmitting fluid circuit in the casing, -means to shift the impeller axially with respect the transmissipn of power through the coupling,

the units of the first set of'vanesd 'the impeller being freely pivoted at their leading edges, and stop means to limit the inclination of the pivoted vanes.

27. In a hydraulic coupling, the combination with a drive shaft and an impeller two. sets of vanes, a driven shaft and a runner, the

runner being attached to said housing, an exte- A shafts, and means for shifting said housing axially for controlling the transmission of' power from the impeller to the runner, the Vunits ofthe rst set of vanes on the impeller being freely pivoted at their leading edges, and stop means to limit the inclination of the pivoted vanes.

-28. An hydraulic transmission including in comb'nation two devices, namely, a. rotary pump. a turbine operated by the uid discharged from the pump and arranged to return the fluid to the pump the impelling surfaces of said pump and the impelled surfaces of said turbine being at fixed angles to their planes of rotation, and a redirector between said two devices, the pump, the turbine and the redirector being co-axiai with one another and the redirector having vanes which are continuous from one edge to the opposite edge and which change thedirection of the fluid in its -passage from one to the other of said devices, said vanes being angularly adjustable automatically when theoutput of fluid increases to a position which diminishes the difference between the tangential components of the velocities of the fluid `at the admission andat the discharge ends respectively of the pump vanes, thustending to maintain constant the net moment of the forces on the pumpwhile permittingV an increase in output to balance an increase in the load on. the turbine.- 29. An hydraulic transmission including in combination two devices, namely, a rotary pump, a turbine operatedby theiluid discharged from the pump and arranged to return the fluid to the pump the impelling surfaces of said pump and the impelledl surfaces'of said' turbine being at fixed angles to their planesof rotation, and' a redirector between said two devices, the pump, the turbine and the redirector being co-axial with one another and the redirectorhaving vanes which are continuous from one edge to the opposite edge and which change the direction of the uid in its passage from one to the. other of said devices, said vanes being angularly adjustable automatically when the output of fluid increases to a positionwhich increases the tangential component of theveiocity of the fluid at the admission end of the pump vanes. 30. An hydraulic transmission including in a turbine operated by the :duid discharged from the pump and arranged to return theiiuid t0 .the pump the impelling surfaces of said pump and the impelled surfaces of said turbine -being at fixed angles to their planes of rotation, and a redirector between said two devices, the' pump, the turbine and the redirector being co-axial with one another and the redirector having vanes which are continuous from one edge to the opposite edge and which change the direction of the duid in its passage from one to the other of said devices and means for diminishing the difference between the tangential components of the velocities of the fluid at the admission and at the discharge ends respectively of the pump vanesautocombination two devices, namely, a rotary pump,

a turbine operated by the uid dischargedv from the pump and arranged to return the fluid to'the pump the impelling surfaces of said pump and.

rior housing longitudinally movable on said.

the impelled surfaces vof said turbine being Y at 75 iixed angles to their planes of rotation, and a redirector between said two devices, the pump, the turbine and the redirector being co-axial with one another and the redirector having varies which direct the iiuid in its passage from the turbine to the pump and thus determine the direction and the tangential component of the velocity of the fluid entering the pump, said vanes being continuous from one edge to the other and yieldingly held to the position corresponding t0 the minimum tangential component and being automaticallyl adjustable by the pressure of the iiuid to increase said tangential component and thus diminish the difference between said tanare continuous from one edge to the opposite edge and which change the direction of the fluid in its passage from one to the other of said deu vices and which when the output of uid increases, diminishesthe difference between the tangential components of the velocities of the fluid at the admission and at the discharge ends respectively of the pump vanes, thus tending to maintain constant the net moment of the forces on the pump while permitting an increase in output to balance an increase in the load on the turbine, said redirector vanes lbeing automatically angularly adjustable to compensate in increasing degree for increases in output.

33. A hydraulic transmission including in combination and co-axially mounted, a pump having impelling blades in xed position thereon, a turbine having driven blades in iixed position thereon, and a redirector having blades between said pump and said turbine which are continuous from one edge to the other and pivotally mounted to vary the angle oi their impelling surface to the planes of rotation of said transmission, and means to vary said angle with changes in relative speeds of said pump and turbine, said pump, turbine and redirector being arranged in a closed series in which the transmission fluid passes through said pump and turbine blades once in each series. l

34.r The apparatus of claim 33 in which said redirector blades are pivoted at their leading edges.

JOSEPH JANDASEK. 

